Apparatus for making precision antivibration mountings



June 9, 1953 F. THIRY 2,641,053

APPARATUS FOR MAKING PRECISION ANTIVIBRATION MOUNTINGS Original Filed Dec. 3, 1943 3 Sheets-Sheet 1 He flee Z'z'al? IN V EN TOR.

jean 75 7311131, BY

H TOFHEY June 9, 1953 THIRY 2,641,053

APPARATUS FOR MAKING PRECISION ANTIVIBRATION MOUNTINGS Original Filed Dec. 3, 1943 3 Sheets-Sheet 2 i i A .93 T

IL l D INVENTOR. X60 7? 722? APPARATUS FOR MAKING PRECISION AN'IIVIBRATION MOUNTINGS L. F. THIRY June 9, 1 953 3 Sheets-Sheet 5 Original Filed Dec. 3, 1943 Patented June 9, 1953 2t stilt? APPAR S FOR MAKING PRECISION ANTIVIBRATION MOUNTINGS "LeonFfThiry, Montclair, N. J as'signorto 'The 'General Tire kit-Rubber Gompany, Akron, Ohio,

a corporation'- of .Ohio

Original application December 3, 1943, Serial No. "512,841, T now Patent No. 2,446,621, dated August 10, 1948.

Divided and this application April 6,1948, Serial'No. 19,308

.6 Claims. (01. 29-235) Thishapplication .is a :division of application Serial No. 512;841, filed iDecernber 3, 1943, and now U. S. Patent No. 2,4.e6,6;21.

The present invention J'relates to vibration mountings -of-=t;he type: employing a pair of relatively rigi dmembers formed ofmetal,. or the like, which are separated by :a :layer of rubber and in which the principal vibration is absorbed by relative movement between the rig-id -members in substantially parallel paths. 'Sucnmountings may comprise either :a pairof spaced concentric members separated' by anrannular sleeve or ring of rubber ortheymaycomprise two or morerelativelyflat plates separated by layers of .rubber. The term r-ubbef as-used herein isiinte'nded to include both natural and synthetic-rubber.

For many purposes it is-essential to successful vibration dampeningto employ vibration .mountings having accurately calibrated deflection rates; that is to say, the amount of displacement-of one of the members of themounting-withrespect to the other for any given load must fall within narrow limits. The deflection characteristic of any given mounting is a function of many iactorsineluding thesize of the various parts, the thickness ofthe rubber layer and the hardness'of the "rubber. The deflection characteristic of mountings is also altered by the provisionof flanges orb-umpers adapted to engage the edge of the rubberlayer and resist relative movementof the rigid members parallel to each other. 'It is also possibleto change the defiectionpurve under Various loads by altering the form and sizeof such a fiangeor bumper. Whilefor any given installation all of these factors may be'selected to-produce-a' mounting of the desired characteristics,*neverthelessin actual commercial production the tolerancespermitted inthesize of the parts, composition'and hardness of the rubber and other -'factors=result in a relatively wide-variation in "the deflection characteristics of mountings that are apparently of identical construction.

Accordingly, it .is the general object of the present invention to provide apparatus for-adlusting the deflection characteristics of vibration mountings after they a are assembled in :order to produce a mounting having the desired: deflection rates.

More specifically, it is the objectof the presen't invention to provide apparatus "forproducing a mounting having *the desired deflection characteristics by permanently mh'anging thellocati'on oi one or more of the "bumper fiangesinthe assem-bledmounting to a predetermineddegree.

Other and more detailed objects and advantages of the invention will become apparent-from the following "specification, the drawings rel'ating thereto anii the claimshereinafter-set forth.

In the drawings, in which like numerals relate to Jcorres'ponding parts in the several Views throughout;

Figures 1, 2 and 3 illustrate three slightly'different types of vibration mountings of the'concentric cylindrical'sleeve type equipped with annular bumper flanges;

Figures 4, 5 and 6 illustrate threestages infithe operation of press-fitting an annular bumper on the inner cylindrical'sleeve of amounting of the type shown in Figures .1, 2 and 3;

Figure '7 shows in fragmentary manner apparatus for determining the proper location of a press-fitted bumper element during the pressfitting zoperation rlEligure 38 shows a slightly different form of :liumpermonstruction,Atogether with a die adapted to alteriits 'formaand location;

.w-Bligure 9:.is :a graph showing "the manner in which the fde'fieetion groove-of amounting may be. varied cbyi varying the position of the bumper flanges;

:Figure .a 1 0. :15: a .tsi'de E'eIeVatiOn. withiparts. in sectioniof aihandLoperated machine'for .press-fitting an :annular bumper ssleeve on the JlIlIlEIvCYl-ll'ldrica'lisleeve tof "'aimountingito the extent required to produce a mounting of exactly the desiredileflection "characteristic;

Figure 11 is :a fragmentary section taken-.on

Figure '12 is :a .fr21pmentary section taken :on theiline I2* l'2jof Figure 11;

Figure-l3 is :a'fragmentary section taken on the: line 1 t3=- l-3 of Figure 10;

Figurerl l isiasideelevationrwith parts in sectiontof-ia. machine -similarto that. illustrated in Figure 10 but adapted to operate .;by hydraulic pressure under the control of the operator;

Figure v15 is :a diagrammatic illustration .of meansadapted tosbeincorporated in the machine of Figure 14=to efiectan automaticstoppage of Ithe bumpcr moving operation;

vIn r-E'igures 31 to r 3 there isv illustrated one form of'tvibrlatiomimountingito which the presentinvehtionsis:applicable,(namely, amounting comprising a "pairmi nconcentric members in the formsof-pylindrioal sleeves separated by-em annular "ring :ofirubb'er. rAs lshown in Figure 1, the annular: rubber ring It .iSIDOSltlOHEBd between an innerzsleeve llandan-outerisleeve [2. The rubbersis preferablyiheltl in ijposition by-a -mechanical bon'd; ithat is tosay, by thepressure ind-uced .abycdistorting ea vulcanized ring of rubber which, its cfreeistat'e, is of lthe'fform illustrated inafthefsuperimposedridotted outline it on- Figure l. tflt'heiirubberiringlisreompressed radially and allowed ito-iexpand :axialiy to the final assembled form rillustratediin solid -.lines,-.aan'd the tendency 3 of the rubber to return to its initial form creates a strong mechanical bond between the rubher and the cylindrical sleeves. While this type of bond is preferred, it will be appreciated thatthe rubber ring may be bonded in the final form by vulcanization, if desired. In this type of vibration mounting, the principal freedom of movement between the sleeves is in an axial direction. In order to restrict relative axial movement between the two sleeves, it is customary to provide bumper rings, or flanges, such as the ring 14 press-fitted at the upper end of the inner sleeve H and the inturned flange [5 formed on the lower end of the outer sleeve l2.

In the mounting of Figure l, the bumpers are provided only on the upper end of the inner sleeve and the lower end of the outer sleeve, inasmuch as the mounting is intended to act as a support for a member mounted on the inner sleeve and, consequently, the principal forces are acting in a downward direction on the inner sleeve and an upward direction on the outer sleeve. It will be appreciated that the bumper rings or flanges may both be formed in the manner of the flange I5 in Figure l, or, as shown in Figure 2, the flange [So on the outer sleeve may be formed as a press-fitted ring. Where the mounting is to sustain forces which act substantially equally in opposite directions, bumpers, such as the bumpers Id and l5a in Figure 3, are provided on both ends of both sleeves.

Due to tolerances in the outside diameter of the inner sleeve, the inside diameter of the outer sleeve and in the size of the rubber ring in its free state, it is found that there are unavoidable variations in the axial extent of the distorted rubber ring In in the finally assembled mounting. These variations result in a variation between the deflection of different mountings under a given load. In addition, unavoidable and minor variations in the composition or hardness of rubber likewise result in different deflection rates for different mountings which are otherwise apparently identical.

In accordance with the present invention, these variations are corrected and a plurality of mountings having identical deflection characteristics is readily produced by adjusting the position of one or more of the bumper rings of the mounting after the rubber ring is inserted between the two sleeves. The effect of such adjustments is best illustrated in the chart, Figure 9, in conjunction with the fragmentary illustrations in Figures 4 to 6, inclusive.

Figure 9 shows a graph of axial force acting upon one of the sleeves plotted against the axial deflection of that sleeve with respect to the other sleeve. The axial deflection curve for any given mounting varies widely in form, depending upon the proportions of the various parts, but the curves illustrated in Figure 9 are generally representative of the nature of the changes in deflection rate that can be achieved by adjusting the position of the bumper rings. The lowermost curve 20 represents the deflection curve of a mounting of the type mentioned when no bumpers are employed. If after assembly a bumper ring, such as the ring 2| in Figure 4, is pressfitted on the inner sleeve II by means of the plunger 22 of a suitable press until the ring assumes the position shown in Figure 4, in which it is spaced slightly from the end of the rubber ring In, the deflection curve for the mounting will be for a portion of its length identical to the mounting having no bumpers, but after the rub- 4 bar contacts the bumper ring the resistance to deflection will increase, with the result that the deflection curve will assume a form somewhat like that shown at 24 in Figure 9.

By pressing the bumper ring 2| onto the inner sleeve until it just touches the rubber ring II, as shown in Figure 5, a deflection curve represented by the line 25 in Figure 9 may be secured. The stiffness of the mounting may be further increased, with the result that it has a. deflection curve such as that illustrated at 26 in Figure 9, by forcing the abutment ring 2| to a further extent onto the inner sleeve as best shown in Figure 6. It will be apparent, therefore, that it is possible to increase or decrease the stiffness or any given mounting by adjusting the position of the bumper, as above described, over a much wider range than the unavoidable variations in stiffness which result from tolerances of manufacture.

The deflection resistance may be either increased or decreased, depending upon the direction in which the bumper is shifted, but, inasmuch as it is somewhat easier to move the bumper toward the rubber, it is preferred to design and construct the mountings to have resistance to deflection for their rated load slightly less than that desired in the final mounting. In such case, as a last step in the manufacture, one or more of the bumpers is adjusted in position to increase the stiffness of the mounting to the degree necessary to produce a mounting of the desired deflection characteristic.

For some purposes, where it is determined that the desired deflection characteristic can be achieved with the required accuracy by adjusting the flange until it just contacts the end of the rubber ring, it is possible to carry out the method in an ordinary hand-operated or manually controlled mechanical press which will force a press-fitted ring onto one of the mounting members until the desired relationship is achieved. The operator may, by inserting a very thin feeler gauge between the end of the rubber and the bumper, ascertain when the bumper has just contacted the rubber. If a slight space between the rubber and the bumper is desired, a feeler gauge of appropriate thickness can be employed and the pressing operation stopped when the bumper reaches the desired position.

In Figure '7 is illustrated a fixture for determining the proper location of a bumper particularly adapted for use in cases where the bumper is forced into the body of rubber, as indicated in Figure 6, to produce a stiffness represented by the line 26 on Figure 9. In Figure '7 numeral 30 represents the bed of an ordinary press having a plunger 3| adapted to force the abutment ring 32 onto the inner sleeve ll of the mounting. Mounted on the bed 30 of the press is an upright post 33 having a hinged section 34 at its upper end, upon which is mounted a conventional form of dial indicator of the type commonly used for indicating minute dimensional variations. An arm 36 pivoted at 31 on the member 34 underlies the plunger 38 of the dial indicator and has a downwardly bent extremity carrying a button 39, which rests upon the upper end of the rubber ring H) of the mounting. As a result of this arrangement, as the bumper ring 32 is forced downwardly beyond the point at which it first contacts the rubber ring I0 it will cause an upward flow or extrusion of the rubber in the manner illustrated in Figure 6, which will tend to lift the button 39 and lever 36, thereby raising the plunger 38 of the indicator 'andicausing "the'pointer of the indicator to traverse the dial, therebygi-ving an indication of "the amount which the upper end of the rubberring has been elevated. By stopping the operation'o'f the press 'aftertherubber ring has been elevated 'by a predetermined amount, it is possible to obtainmountings of relatively uniform deflection characteristics.

The fixture illustrated in Figure '7 may also be employed intheisamemanner in connection with mountings in which the bumper is anintegrally formed .fiange onone of the sleeves. Thus, in the -case of such a .mountingillustrated in :Figure 8, the inwardly .bentflan'ge 42 on the inner sleeve 43 may be bent downwardly to a greater extent by means ofia die of appropriate shape which is mounted upon the plunger of the press. The die '44 hasa stem 45 which will projectiontirely through the inner tubular member -43 :before any deformation-of thei flange-42 occurs, thus preventing collapse of theiinner tubular member, which is supported on a support 46. The operator, as in the case of the mechanism :illustrated in Figure 7, will cause the die 44 to "move downwardly until the upward extrusion of the rubber ring reaches the predetermined amount, as indicated by the dial indicator of .Figure '7.

In Figure is-illustrated a mechanism for adjusting a bumper to thedesired point for use in cases where it is necessary to produce mountings whose deflection rates are very accurately calibrated. In this mechanism control means are provided which give a direct reading of the amount of deflection under a rated load throughout the bumper moving operation, thus enabling the-operator to stop the machine when the defiection reaches the desired value.

Referring to Figure 10, the mechanism comprises a U-shaped frame 50, the lower leg 5! of which forms the base of the machine and the upper leg 52 of which supports a hand-operated screw press. While the mechanism of the press may take any suitable or conventional form, there is shown, for purposes. of illustration, a press comprising a hand wheel 53, the hub of which is threaded upon a threaded arbor 54 the upper end of which is reduced at 55 and fitted within an opening 5-6 in the upper leg 52 of the frame. Any suitable means may be provided for fixing the stem of the arbor 54 in the opening 56 against movement relative to the frame.

Mounted on the lower side of the hub-of hand wheel 53 is a thrust bearing assembly'comprising a pair of plates '51 and 58 separated 'by roller bearings and held in assembled relation by means of a housing 59, which is fixed at its upper end to the hub of the hand wheel. The lower face of the plate 58 is provided with a recess 60 adapted to receive the annular bumper 6|,which is to be press-fitted on the inner sleeve ll of the mounting. A ring of rubber 62 maybe provided within the .recess 60 to grip the bumper, GI and hold it in position prior to the press-fitting operation. In some cases it'may be preferred to start the press-fitting operation in another press and complete the operation in the machine of Figure 10, In that case the bumper will be "on the sleeve ll when the mounting is placed in. the machine and it will be unnecessary to provide the recess 60 or its rubber ring 62.

The threaded arbor 54 is'providedwith a con tr al bore 63 having a countersunkenlargement 64 in its lower end. Positioned within the countersunk enlargement 6-4 is aclamping plunger B5 which projects freely through suitable openings in the p1ates'51and 58 of thethrustbearing'and is adapted to pass freely through the bumper ring'fil. Thelower end of'the'plunger GEisprovided with a rounded pilotprojection 66, which is adapted 'to enter the upper end of inner'sleeve H :and bring the sleeve intouproper alignment with the plunger .65. The annular shoulder .61 on the lower'end of the plunger '65 is adapted to abut theupper endofthe sleeve H and 'hold'the sleeve against its flower support, hereinafter'described.

'iPlunger G5 is connected to a rod '68, which passes through the bore 63 in the arbor 54-and carries at its upper end a nob-or handle 59. The upper end of thereduced portion 550i thearbor is split and provided with a pair of projecting ears Ill and H, as best shown in Figure 12. 'A bolt '72 passes through the cars 10 and 1|,and threaded on the opposite-end thereof is a 'nut 13 carrying a handle "14 for rotating the same. The arrangement is such that when the handle 74 is raised into the dotted 'line position shown in Figure 10 the rod 68 will be released, thereby permitting the rod -and its attached plunger 65 to drop by gravity into the lower dottedlineipcsition-shown byFigure 10, in which position the pilot line 66 has entered the sleeve H and the plunger is resting on the topedge of the sleeve. In this position, the rod 68 'may be clamped by pulling the handle 14 downwardly into the solid line position illustrated. When the plunger and rod 68 are in their upper positionsgtheyma-y also be held against downward movement by shifting the handle 14 to its lower position, thereby clamping the rod 68 within the split upper end of the reduced portion 55 of the arbor.

The outer sleeve l2 of the vibration mounting is adapted to rest upon an annular ring 80, which is pivotally mounted on a lever'B l ,which, in turn, is journaledon a pin 82 carried by the base portion 5| of the frame. Roller bearings83 are preferably employed at this pivot to-reduce friction. The pivotal connection between the ring and the lever 8| is-of such character as to permit limited pivotal movement of the ring 80 with reference to the lever 3! about an axis perpendicular'to the paper in Figure 10 and intersectingthe axis of the mounting. This pivotal connection comprises a pair of projections '84 projecting inwardly from opposite sides of a circular opening 85 of lever 8| within which the ring 80 is positioned. 'The upper surfaces of the projections 84 are V-shaped, as best shown in Figure '12, and are thus adapted to act as fulcrums for the ring 80. The ring 80 is provided with apair of inverted U-shaped projections 86 having the notches 81 adapted to receive the fulcrums 84. The internal angle of the V notch 81 isslightly greater than the internal angle of the V-shaped projection on the fulcrum 84, with the result that a limited pivotal movement of the ring 80 with respect to the lever 81 is permitted.

The lever 8| projects to the left of its pivot 82 and at its extremity carries a pivoted rod '90 adapted to support a .plurality of weights 9| of the type frequently employed in weighing scales.

The right-hand extremity of the lever 8| is connected by means of a turnbuckle linkage 92 to a pointer 93, which is pivoted at 94 on the frame 50 and is adapted to move'over 'ascale 95. Means are provided for holding the lever 8| against movement'in response to the force exertedby the weights '9]. Thismeans comprises a shaft 96 journaled on the frame portion I and having fixed thereto a member 91 having a projection 98, which, in the rotative position of the shaft illustrated in the drawings, engages beneath the left-hand end of the lever BI and holds. that end of the lever against downward movement in response to the force exerted by the Weights. A handle 99 fixed to the shaft 96 is provided for moving the projection 98 out of contact with the lever BI and thus permitting the weights to take effect. The turnbuckle 92 is so adjusted that the pointer 93 is on the zero point of the scale 95 when the stop 98 engages the lefthand end of lever 8|.

The lower end of the inner sleeve II of the mounting projects through the central opening in the ring 80 and is adapted to engage a cylindrical supporting element I02, which is slidable within a cylindrical opening I03 carried by the frame portion 5I. Beneath the cylindrical supporting member I02 is located a horizontal shaft I04 journaled in the frame portion 5 I and carrying an eccentric cam I05, which is adapted to engage the lower end of the cylindrical supporting member I02. A handle I06 is fixed to the shaft I04 and carries a weight I01, which is adjustable along the length of the handle in any suitable manner, as by a set screw I08, which may be threaded into engagement with the handle at the point it passes through an opening in the weight I01. The arrangement of the weighted handle and the eccentric cam is such that when the handle I06 is shifted to the left, as shown in solid lines in Figure 10, the upper end of the cylindrical support I02 is out of contact with the lower end of the inner sleeve II. When the handle is swung counterclockwise about the shaft I04, the eccentric cam I05 elevates the cylindrical support I02 into contact with the lower end of the sleeve II. The weight I01 is so adjusted on the handle I06 that it will exert sufiicient turning force to elevate th cylindrical member I02 into engagement with the sleeve I I. The angle of the cam I05 is such that no amount of force exerted on the top of the cylindrical member I02 will cause the cam to rotate in a direction to lower the member I02.

The sliding support I02 and the eccentric cam and handle arrangement are provided solely for the purpose of automatically compensating for unavoidable variations in the distance between the lower end of the outer sleeve I2 and the lower end of the inner sleeve II of the mounting. If this distance in the manufacture or" mountings is accurately maintained at the same value, the supporting member I02 may be fixed in such a position that it will just contact the lower end of the sleeve II when the outer sleeve rests on the ring 80 and the stop 98 is engaged below the lefthand end of lever 8I. In this case, the eccentric cam and handle for operating the same may be omitted and the support I02 may be fixed in the desired position.

The operation of the mechanism shown in Figures 10 to 13 is as follows: With the parts of the machine in the solid line positions illustrated, a mounting is placed upon the annular ring 80 in the position shown and the handle 14 raised to release the rod 68 and permit the plunger 65 to fall by gravity into contact with the upper end of sleeve II. As soon as this has been achieved, handle 14 is lowered to lock the plunger 65 in position. The weight of the plunger and rod 63 is not sufficient to cause any significant axial deflection of the inner sleeve relative to the outer sleeve of the mounting. As soon as the plunger 65 is clamped in its lower position, the lever I05 is swung counterclockwise toward the dotted line position in order to elevate the supporting member I02 into engagement with the lower end of the inner sleeve II. This positively locks the inner sleeve I I in a fixed position. Stop 98 is then moved out of contact with the lefthand end of lever 8I by swinging handle 99 counterclockwise, thus permitting the force exerted by the weights 9I to exert a counterclockwise rotative force upon the lever 8 I. The only resistance to such rotation of the lever 8I at this time will be the resistance offered by the rubber ring I0 positioned between the sleeves iI and I2 of the vibration mounting and, consequently, the lever 8| will rotate by an amount which accurately measures the axial deflection between the sleeves incident to the axial load applied by means of the weights 9I and the lever 8I to the lower end of the sleeve I2. The amount of this deflection will be indicated by the position of the pointer 93 on the scale 95. This deflection will purposely be slightly greater than that desired and, consequently, the pointer will assume a dotted line position at a point on the scale above that marked by the adjustable indicator IIO, which is set at the desired deflection for the load employed. The operator is now ready to begin the operation of pressing the annular bumper 8| onto th inner sleeve I I, which operation is accomplished by rotating the hand wheel 53, thereby forcing the plate 51 of the thrust bearing downwardly and causing the ring 6| to be pressfitted onto the upper end of the sleeve II. As the operator continues the pressing operation he observes the pointer 93 and the operation is stopped at the instant that the pointer reaches the point on the scale marked by the adjustable slide Hi). All of the parts of the machine may be then returned to their original positions in the reverse order and the mounting removed from the machine. The mounting will then be complete except that it will usually be necessary to trim off an excess projection on the bumper ring 6| in order to produce a flush end on the inner sleev II.

While the machine illustrated in Figure 10 is constructed for use in press-fitting separate abutment sleeves on the inner sleeve of the mounting, it will be apparent that it may be readily adapted to press an abutment ring on the outer sleeve. Moreover, in place of pressing the separate abutment ring on one of the sleeves of a mounting, th machine may be equipped with a die similar to the die 44 in Figure 8 for the purpose of changing the position of an integral abutment flange on either of the sleeves. In this case, the stem 45 of the die 44 in Figure 8 will be substituted for the plunger 65 of Figure 10, and the flange bending portion of the die will be made 2; a separate annular piece secured to the plate In Figure 14 is illustrated a hydraulically operated mechanism generally similar to that illus trated in Figure 10 but employing an external source of hydraulic power for its operation. In this machine the control means may either operate an indicator which will indicate to the operator when the machine should be stopped, or it may, as shown in Figure 15, automatically stop the machine when the deflection characteristic of the mounting reaches the desired value.

The machine of Figure 14 includes a generally U-shaped frame I20, which, as illustrated is of enemas hollow cast construction. Pivoted on apin I2'I fixed to the-frame" I20is a-lever I22 similar in construction and operation to the lever 8| of Figure 10. The left-hand end of lever I22 is pivotally connected to a rod I23, which supports a plurality of weights I24.

To the right of pivot I2I lever I22'pivotal1y supports a ring I25, which is similar in construction and mode of operation to the ring 80 of Figum 10 and which is-adapted to support a vibrat'ion mounting of the type under consideration by engagement with the lower end of the outer sleeve I2 of the mounting. The inner sleeve II of the mounting projects through a central opening in the ring I25 and is adapted to engage a cylindrical supporting element I26, which rests upon a spiral cam I2'I pivoted on a shaft I28 carried by the frame.

Fixed to the cam I2? is a lever I 29, which is normally urged upwardlj/ by a light spring I 30. The spring I35 has sufficient strength to raise the lever and thereby elevate the cylindrical supporting element I26- into contact with the lower end of the sleeve I I, but is not sufficiently strong to lift the mounting from its position resting upon the ring I25.

The right-handend ofthe lever I22 projects through anopening I-34-formed in the inner side of the upright portion of the frame I20 into the interior of the hollow upright portion, and within the hollow frame it is connected by means of a turnbuckle link- I35 to a pointer I36, which is pivoted between a pair of ears I5'I formed on the frame at opposite sides of the opening I34. The pointer I36 is adapted to cooperate with a scale I38 having an adjustable indicator I35 associated therewith. At the left-hand side of the machine a hand lever M is-fixed to the shaft I4I, which, in turn, is journaled on the lower portion of the frame I20. The shaft I4I carries a stop I42 which engages beneath the left-hand end of the lever I22 and holds the lever against counter-clockwise movement in response to the force exerted by the weights I24. The arrange-- ment of the stop I42 issuch'that it does not release the lever I22 until after the handle I it has been swung counterclockwise through an arc sufficient to actuatethe plunger operating mechanism hereinafter described.

Formed integrally with the upper portion of the frame I20 is a cylinder I44 having an integrally formed upper end wall I45and a removable cylinder head Hit. A hollow piston rod I4l extends through both ends of the cylinder and carries an integrally formed piston I45. upper" end of the cylinderis provided with any suitable or conventional form of packing gland I49 and "a fluid inlet pipe I50. A spring II is provided within the cylinder for urging thepiston I48 upwardly at all times, the spring being strong enough to elevate the piston and'discharge the fluid in the upper end of the cylinder when the inlet Ht is connected to the low pressure return line, as hereinafter more fully described.

The lower end of the hollow piston rod I4'I is threaded to receive a ring I52, which is provided with a counterbore. IE5 at its lower end adapted to receive an abutment ring I54 similar to the ring of Figure and ring 25 of Figures i to 6. The counterbore I53 is larger in diameter than the ring I54 and is provided with a ring I55, of rubber or the like, which serves to filetionally hold the ring I54 in position within the counterbore. As in the previous. machine, if the ring I54 is partially pressed on the sleeve I I prior The to the final adjustment made in the machine of Figure 14, the counterbore I53 and the ring I55 may be omitted.

Mounted withinthe hollow piston rod I4! is a plunger I55, to the lower end of which is removably secured a head. I15? having a rounded end portion I58 adapted to fit within the upper end of the inner'sleeve I I of thevib'ration mounting and align the mounting with the ring I54.

The outer diameter of. the plunger head I5! issubstantially equal to the internal diameter of the ring I54, but will pass freely through the latter.

The machine may be adapted to operate upon abutment rings of? various sizes by removing the ring I 52 and the plunger head I 5'I and substituting a ring and plunger head of suitabledimen-- sions.

The upper end of the plunger I56 is provided with an ear IE5 carrying a transverse pin I6I,

which projects into the slightly elongated slot I52 in the end of a lever I53. The lever I63, in

turn, is pivotally mounted upon a transverse pin. I54, which extends between a pair of upstanding ears I55 on the upper portion of the frame I20.

The right-hand end of the lever I63 is provided with a generally downwardly extending cylindrical bore I56 containing aplunger I51 having a semispherical recess I58 in itslower lever m3 and a seat I'I'I formed integrally with and extending between the upstanding ears I65 of the frame I29. is to urge the lever I63 at all times in a clockwise direction and thus keep the piston rod I99 in a state of compression between the plunger I67 and the piston I'II. The lower end of the cylinder I72 is provided with a fluid inlet pipe I for admitting operating fluid to the cylinder and the spring I15 is suillciently strong to return the cylinder M2 to its lowermost position and discharge theiiuid in the cylinder when the inlet I89 is connected to the low pressure return line, as hereinafter described.

Any suitable hydraulic control mechanism may be employed to control the admission of fluid to cylinders I72 and M4. The particular means illustrated is adapted to operate these cylinders in succession, and their operation is correlated with the withdrawal of the stop M2 to the end that the stop will be withdrawn after the cylinder' H2" and before cylinder I44 are operated. This means; as best shown in the drawings, comprises a pair of valves I82 and I33 which is mounted upon a panel I84 fixed in any suitable manner to the left-hand side of cylinder I44. Valves I82 and I53 are conventional valves of the type employing an internal rotary valve member mounted upon a stem which projects from the valve housing.

The stem I85 of valve I83 carries a V-shaped operating member'IBB having a pair of fingers I83 and I88 extending at an angle of approximately 90 to each other; Thestem I92 of valve I52 carries a similar V-sh'ap'ed operating mem- The action of the spring I15 11 ber I9I having fingers I92 and I93. The panel I84 with the two valves and their operating members I86 and I90 are located to the rear of the plane of movement of the operating handle I40, as viewed in Figure 14, the handle being broken away to show the valves.

Valve I82 controls the operation of cylinder I12, to which it is connected by means of a pipe or conduit I94 that extends from the valve to the inlet port I80 of the cylinder. Similarly, valve I84 controls the operation of cylinder I44, to which it is connected by means of pipe or conduit I95 that is connected to the inlet port I50 of cylinder I44. The pipe I91, which is connected to any suitable source of fluid under pressure, not illustrated, is connected to the valve I82 and by a branch line I98 to the valve I83.

An exhaust or return line 200, which is connected to any suitable low pressure reservoir of fluid, is also connected to the valve I82 and, by a branch line 20I, to the valve I83. The construction of the valve I82 is such that when the stem I90 and the stem operating member I9I are in the position illustrated in Figure 14, communication through the valve is provided between pipe 200 and pipe I94 while th pressure line I91 is blocked at the valve I82. When the stem I90 is rotated counterclockwise through an angle in the order of 90, the valve connects pressure line I91 to conduit I94 and the line 200 is blocked at the valve. Valve I83 is identical in construction, and in the position illustrated it connects pipes 20I and I95 while blocking line I98. When the stem I85 is rotated counterclockwise approximately 90", valve I83 connects lines I98 and I95 while blocking line 20I.

Valves I82 and I 83 are operated by a finger 203 carried by an arm 284 which projects rearwardly from and is fixed to the handle I40, with the result that the downwardly extending finger 203 lies in the plane of the valve operating members I86 and I9I. As a result of this arrangement, when the handle is shifted to the right into its stop position illustrated, finger 203, by engaging fingers I88 and I93 of the valve operating members I86 and NH, shifts both valves to the positions illustrated in which they connect both cylinders to the low pressure return line.

When the handle is shifted to the left, as viewed in Figure 14, finger 203 will first contact finger I92, thus shifting the valve I82 to a position in which it connects cylinder I12 to the pressure line I91. Thereupon, further movement of the handle I40 to the left will cause the finger 203 to engage the finger I81 and shift valve I83 to a position in which it connects cylinder I44 to the pressure line I91. The stop I42, which is also movable with the handle I40, is so positioned that it will release lever I22 intermediate the shifting of valves I 82 and I83 during counterclockwise movement of the handle I 40.

In order to provide a slow downward movement of the piston I48 without affecting the speed of return movement of the piston, any suitable form of throttle or speed control valve, such as the valve indicated diagrammatically at 206, may be employed in the pressure line I91. Valve 206, by throttling the flow of fluid under pressure, will cause the piston I48 to move slowly in a downward direction, but since the return line 200 is not restricted the return movement of the piston I48 under the influence of spring II will be rapid.

The operation of the mechanism shown in Figure 14 is as follows. The operator, after inserting the abutment ring I54 within the recess in ring I52 with his right hand, places his right hand on lever I29, thus forcing it downwardly against spring I30, and at the same time rests the vibration mounting on the ring I25.

As soon as the mounting is in place, the operators right hand is removed from the lever I29, thus permitting the spring I30 to lift the lever and raise the cylindrical supporting member [26 into contact with the lower end of the inner sleeve I I. The operator then with his left hand swings the handle I40 to the left, which movement first shifts valve I82, thus admitting fluid under pressure to cylinder I12 and causing the plunger I56 with its head I51 to move downwardly. The rounded pilot end I58 on the head I 51 enters the upper end of the inner sleeve I I and thus properly locates the sleeve in alignment with the abutment ring I54. To facilitate this action the permissible pivotal movement of ring I25 relative to lever I22 is not sufiicient to permit the upper end of the mounting to tilt so far that the pilot I58 cannot enter sleeve I I. Continued movement of the handle I40 to the left withdraws the stop I42 from beneath the lever I22 and thereafter shifts valve I83 to permit fluid under pressure to enter the upper end of cylinder I44, thus causing the piston I48, ring I52 and the abutment sleeve I54 to move downwardly and press fit the abutment ring upon the upper end of sleeve I I.

The arrangement of the stop I42 is such that it holds the lever I22 in such a position that the pointer I36 is at the zero point on the scale I38. When the supporting cylinder I26 is elevated by lever I29 into contact with the lower end of sleeve II, member I26 constitutes a fixed support which positively rotates the sleeve I I in such a position that at no load on the outer sleeve I2 will the pointer I36 remain at the zero position on the scale I38.

When the plunger I56 moves downwardly against the upper end of sleeve II, the force exerted by the plunger cannot cause a downward movement of the supporting member I26 because the angle of the cam I21 is insufficient to permit a return movement. Consequently, when the lever I22 is released and the load induced by weights I24 applied to the outer sleeve I2 of the mounting, the pointer I36 will move upwardly on the scale I38 and accurately indicate the total axial deflection of the sleeve I2 under the influence of the force applied. As previously indicated, this deflection, in the normal case, will be slightly in excess of that desired and, consequently, the operator will permit the downward movement of the piston I48 until the pointer I 36 swings downwardly to the point indicated by the adjustable slide I 39 on the scale I38, the position on the slide indicating the desired deflection.

As soon as the pointer reaches this position, the handle I40 is swung to the right, thus shifting valve I83 and connecting the upper end of the cylinder I44 to the low pressure return line 200. This immediately results in the return of the piston I48. Continued movement of the handle I40 to the right shifts the stop I42 into position beneath the lever I22, thereby raising the lever and relieving the load upon the mounting.

The final movement of the handle I40 to the right connects cylinder I12 to the low pressure line 200, thereby permitting the spring I 15 to ele vate the plunger and release the mounting. The parts are then in position to repeat the cycle of operation as just described on another mounting.

As previously indicated in connection with the enemas "mechanism of Figure .10, thezmechanismioi Figure 14 may also be employed to shiftxtheposltion of integral abutment flanges, such'asithose illustrated in Figure 3. It is only-necessary to connect the spindle .45 :on the die'M'ofFigure '8 to the plunger I56 :andlto connect-the-outerzannular portion of the .die' d lpwhichwill be aseparate annular piecatto the hollow. pistonxrodi M1.

The left-hand end of the frame I20'is1pr0- vided with awallLZ I I) having an internal vertical surfaceZI I, which is'adapted to engage the lower end I I2 of the handle I48 in order-to limit movement of the handle in a clockwise direction .to the position illustrated in the drawings. Thezupper portion of: the wall. 2 I is provided with an inclined surface I F3 for limiting counterclockwise movement of the handle I40.

It will be appreciated thatthe details ofconstruction of the mechanism "may bevaried widely without departin from the spirit of the invention. Thus, instead of employing springs to return the pistons H8 and Ill], the cylinder and piston units may be made double-acting under ventional form of means for giving the :piston I48 on its downward stroke :a high speed for the initial portion of the stroke and a low speed'for-the final portion, during whichthe press-fitting'operation is performed.

In order to adjust the machine to accommodate mountingsof difierent axial length, it is only necessary :to insert suitable spacers betweenthe outer sleeve I2 and the ring I25, or, if preferred, the vertical portion of the frame I28 may be made adjustable as to height in order to accommodate mountings of different lengths.

As previously indicated, the control means, instead of indicating to the operator when the mounting has the desired deflection characteristic, may automatically stop the-machine and, accordingly, there isillustrated in a somewhat diagrammatic manner in Figure .a suitable electromagnetic means whichmay be incorporated in the machine of Figure 14 to -accomplish that result.

Referring to Figure 15, there is shown a valve H33 which issubstituted for the valve Itirof Fi ure 114 when automatic operation is desired.

Valve i83 contains awspooltZIII having a groove .2 I I vfor controlling flowof fluid through'thevalve. To the valve are connected-the previouslymenvtioned line I29! from a-source of fluid under pressure and the line 2%, which-is a return line to a gized and thespool elevated againstthe force of spring 2I2, communication"between lines I95'and 12610 is blocked and the fluid is iree'to'flow'from line IE! to line I95 in .order'to cause downward movement of the :piston I48 ofsFigure 14.

The electrical'energy forz'actuating the solenoid 2I3is supplied from any suitable source of electric power by a pair of lines 2 and 2I5, line 2M beingdirectlyconnected to one end of the solenoid coil and line 2I5 being connected to the otherend through a switch '2I6, line 2H,

conductive "material.

.IS? :to line I andthereby starts the downward orbumper movingstrokeiof the piston I48. .Duringithis operationtheswitch arm 2 I8, whichconnects lines 2!? andrZIB, is held closed bymeans oiia spring 220.

Means are provided for opening switch '2 I8 and thereby interrupting the circuit through the solenoid 2I3 when the deflection characteristic =01 the mounting reaches the desired amount. This means includes a solenoid :22! having an armature '226 which project entirely through .to-the coil of the solenoid. The armature226 is operatively connected to the switch 2 I8 and .the lower end of the armaturent. carries a bara221, which adapted upon downward movement'of theiarmature to close an electric circuit between a pairtof contacts 223 and 229. The'circuit for'the solenoid 22I includes a line 222, which connects to line'ZI'I, and a line'223, whichis connected to the pointer I36, which corresponds to the pointer i36 of Figure 14.

The pointer in this case is madeof electrically An arcuate member I38 carries-an adjustable slide I39'-. upon whichis positioned a contact'224 adapted to cooperate with .a contact 225 on the pointer I36.

The member I38 corresponds to the scale IE8 or Figure 14, and the slide I39 corresponds to the adjustable indicator I39. Thearcuatemember I38 is electrically connected by means of a wire--23I'to the :line 214.

When the pointer-136 swings to-a position in which the contact 225 engages the contact 1224,

it is apparent that the circuit'through'thesolenoid MI is completed from line 222 through'the solenoid and-thence through line 223, pointer contacts .225 and $24, members I33 and I39 and line .2'3I to the line 2 I4. The circuit thus completed energizesthe solenoid and causes the armature 226 -to move downwardly, opening switch 2 i8 and-engaging the bar 221 with the contacts 228 and 228. As soon as switch H5 is opened, the current isiinterrupted at the main solenoid 2I3 and the spool of valve I33 returns to the position shown in the drawings, thus stopping the operation of the press.

The contacts 228 and 229 and the bar 221 provide a holding circuit to insure that once the solenoid 22I isenergized by engagement of contacts .224 and 225, it will remain energized until the manual switch 2H5 is opened. Thus, contact .223 is connected to the line 223 and contact 22915 connectedto the line Eli. As a result of these connections-current from the solenoid 22I may'iiow through lineflll, contact 223, bar 221, contact are and line 23I to theline 2, even though the contacts 224 and :225 do not remain nrengagement.

The operation of the "machine of Figure 14, when it incorporates the automatic shut ofi mechanism of Figure 15, is-believed to be ap- :parent 'fromthe above-description. It-may .be

noted that as in the case of the operation described in connection with Figure 14, the machine is started by swinging handle I to the left. The first portion of this movement, as previously described, shifts valve I82 to actuate the clamping plunger I56. Thereafter, further movement of the handle I40 withdraws the stop H2 and the final movement closes the switch 216. Between the time that the stop M2 is removed and the time that the switch H6 is closed by handle I40, the load will be applied to the sleeve I2 of the mounting, thus causing the pointer I36 to swing upwardly until its contact 225 is located above the contact 224. During the passage of contact 225 over the contact 224, solenoids M3 and 22! will remain inactive due to the opening circuit of switch 2| 6. Thereafter, as soon as switch 2H3 is closed, solenoid 2|3 will shift valve I83 and start the operation of the press, which operation will continue automatically until interrupted by the solenoid controlled switch 2 l8, which is actuated when the deflection characteristic of the mounting reaches the predetermined amount.

It is apparent that there is provided in accordance with the present invention simple and practical methods and apparatus for producing vibration mountings of accurately calibrated deflection characteristics. While the invention is illustrated and described in connection with mountings of the type employing a pair of concentric rigid members, it will be appreciated", that the principles of the invention are equally applicable to any type of vibration mounting incorporating a pair of rigid members separated by a layer of resilient rubber.

It is apparent, further, that while several mechanisms are illustrated and described, further modifications of the mechanisms are available within the spirit of the invention and the scope of the appended claims.

What I claim is:

1. An apparatus for positioning a bumper on one of the members of a vibration mounting of the type consisting of inner and outer concentric radially spaced members separated by an annular ring of rubber to produce a mounting having a predetermined deflection for a, given load comprising a frame, a substantially horizontal lever pivotally mounted intermediate its ends on said frame and provided with an opening on one side of the pivot point, a weight pivotally suspended from said lever on the other side of said pivot point, a plate horizontally pivoted in said opening on said lever with the pivot axis of said plate being parallel to the pivot axis of said lever, said plate being adapted to support the outer concentric member and provided with a central opening, a supporting element in alignment with the central opening of said plate and providing support for the inner concentric member, a plunger mounted on the frame over said plate for clamping the inner concentric member against the supporting element, a verticallyreciprocable member outside of said plunger for progressively moving a bumper axially on one of the concentric members and against the annular ring of rubber, said plunger being moveable relative to said vertically-reciprocable member, a deflection indicating mechanism for indicating the axial displacement of the outer concentric member, and a stop for preventing extreme rotation of said lever about its pivot point.

2. An apparatus for positioning a bumper on one of the members of a vibration mounting of the type consisting of inner and outer concentric radially spaced members separated by an annular ring of rubber to'produce a mounting having a predetermined deflection for a given load comprising a frame, a substantially horizontal lever pivotally mounted intermediate its ends on said frame and provided with an opening on one side of the pivot point, a weight pivotally suspended from said lever on the other side of said pivot point, a plate horizontally pivoted in said opening on said lever with the pivot axis of said plate being parallel to the pivot axis of said lever, said plate being adapted to support the outer concentric member and provided with a central opening, a supporting element in alignment with the central opening of said plate and providing support for the inner concentric member, a cam mounted on said frame in turn supporting said supporting element provided with means for rotating said cam to raise said supporting element to compensate for variations in the distance between the bottoms of the inner and outer concentric members in the unloaded condition, a plunger mounted on the frame over said plate for clamping the inner concentric member against the supporting element, a verticallyreciprocable member concentric with the axis of said plunger for progressively moving a bumper axially on one of the concentric members and against the annular ring of rubber, said plunger being moveable relative to said vertically-reciprocable member, a deflection indicating mechanism mounted between said frame and said lever for indicating the axial displacement of the outer concentric member, and a stop for preventing extreme rotation of said lever about its pivot point.

3. An apparatus for positioning a bumper flange on one of the members of a vibration mounting of the type consisting of inner and outer concentric radially spaced members separated by an annular ring of rubber to produce a mounting having a predetermined deflection for a given load comprising a frame, a substantially horizontal lever pivotally mounted intermediate its ends on said frame and provided with an opening on one side of the pivot point, a weight pivotally suspended from said lever on the other side of said pivot point, a plate horizontally pivoted in said opening on said lever with the pivot axis of said plate being parallel to the pivot axis of said lever, said plate being adapted to support the outer concentric member and provided with a central opening, a supporting element in alignment with the central opening of said plate and providing support for the inner concentric member, a cam mounted on said frame in turn supporting said supporting element provided with means for rotating said cam to raise said supporting element to compensate for variations in the distance between the bottoms of the inner and outer concentric members in the unloaded condition, a plunger mounted on the frame over said plate for clamping the inner concentric member against the supporting element, a vertically-reciprocable member concentric with the axis of said plunger for progressively moving a bumper flange axially on one of the concentric members and against the annular ring of rubber, said plunger being moveable relative to said vertically-reciprocable member, said vertically-reciprocable member being provided with a die for engaging said bumper flange, a deflection indicating mechanism mounted between said frame and said lever for indicating the axial displacement of the outer concentric member, and a stop for preventing extreme rotation. of said lever about its pivot point.

4. An apparatus for positioning a bumper on one of the members of a vibration mounting of the type consisting of inner and outer concentric radially spaced members separated by an annular ring of rubber to produce a mounting having a predetermined deflection for a given load comprising a frame, a substantially horizontal lever pivotally mounted intermediate its ends on said frame and provided with an opening on one side of the pivot point, a weight pivotally suspended from said lever on the other side of said pivot point, a plate horizontally pivoted in said opening on said lever with the pivot axis of said plate being parallel to the pivot axis of said lever, said plate being adapted to support the outer concentric member and provided with a central opening, a supporting element in alignment with the central opening of said plate and providing support for the inner concentric member, a cam mounted on said frame in turn supporting said supporting element provided with means for rotating said cam to raise said supporting element to compensate for variations in the distance between the bottoms of the inner and outer concentric members in the unloaded condition. a hydraulically-operated plunger mounted on the frame over said plate for clamping the inner concentric member against the supporting element, a hydraulically-operated, vertically-reciprocable member concentric with the axis of said plunger for progressively moving a bumper axially on one of the concentric members and against the annular ring of rubber, said plunger being movable relative to said vertically-reciprocable member, a deflection indicating mechanism mounted between said frame and said lever for indicating the axial displacement of the outer concentric member, a removable stop for preventing extreme rotation of said lever about its pivot point, and a single manual control element movable in one direction to successively actuate said hydraulically-operated plunger, remove said stop, and actuate said hydraulically-operated, vertically-reciprocable member.

5. An apparatus for positioning a bumper on one of the members of a vibration mounting of the type consisting of inner and outer concentric radially spaced members separated by an annular ring of rubber to produce a mounting having a predetermined deflection for a given load comprising a frame, a substantially horizontal lever pivotally mounted intermediate its ends on said frame and provided with an opening on one side of the pivot point, a weight pivotally suspended from said lever on the other side of said pivot point, a plate horizontally pivoted in said opening on said lever with the pivot axis of said plate being parallel to the pivot axis of said lever, said plate being adapted to support the outer concentric member and provided with a central opening, a supporting element in alignment with the central opening of said plate and providing support for the inner concentric member, a cam mounted on said frame in turn supporting said supporting element provided with means for rotating said cam to raise said supporting element to compensate for variations in the distance between the bottoms of the inner and outer concentric members in the unloaded condition, a hydraulically-operated plunger mounted on the frame over said plate for clamping the inner concentric member against the supporting element, a hydraulically-operated, vertically-reciprocable member concentric with the axis of said plunger for progressively moving a bumper axially on one of the concentric members and against the annular ring of rubber, said plunger being movable relative to said vertically-reciprocable member, a deflection indicating mechanism mounted between said frame and said lever for indicating the axial displacement of the outer concentric member, a removable stop for preventing extreme rotation of said lever about its pivot point, control means for said hydraulically-operated plunger and vertically-reciprocable member, and a solenoid-controlled switch responsive to the deflection of the deflection indicating mechanism to stop the operation of the vertically-reciprocable member when the deflection characteristic of the mounting reaches a predetermined point.

6. An apparatus for positioning a bumper on one of the members of a vibration mounting of the type consisting of inner and outer concentric radially spaced members separated by an annular ring of rubber to produce a mounting having a predetermined deflection for a given load comprising a frame, a substantially horizontal lever pivotally mounted intermediate its ends on said frame and provided with an opening on one side of the pivot point, a weight pivotally suspended from said lever on the other side of said pivot point, a plate horizontally pivoted in said opening on said lever with the pivot axis of said plate being parallel to the pivot axis of said lever, said plate being adapted to support the outer concentric member and provided with a central opening, a supporting element in alignment with the central opening of said plate and providing support for the inner concentric member, a cam with an increasing radius horizontally pivoted on the frame in turn supporting said supporting element, a handle integral with said cam and extending out substantially horizontally from the thicker portion of the cam, a compression spring disposed out from said cam between said handle and said frame, a plunger mounted on the frame over said plate for clamping the inner concentric member against the supporting element, a vertically-reciprocable member concentric with the axis of said plunger for progressively moving a bumper axially on one of the concentric members and against the annular ring of rubber, said plunger being moveable relative to said vertically-reciprocable member, a deflection indicating mechanism mounted between said frame and said lever for indicating the axial displacement of the outer concentric member, and a stop for preventing extreme rotation of said lever about its pivot point.

LEON F. THIRY.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date Re. 18,843 Skillman May 30, 1933 207,245 Britton Aug. 20, 1878 376,541 Mergenthaler Jan. 17, 1888 440,938 Anthoni Nov. 18, 1890 493,784 Reeser Mar. 21, 1893 1,734,025 Zeibig Oct. 29, 1929 1,827,267 Short Oct. 13, 1931 1,913,933 Lamborn et a1. June 13, 1933 1,959,254 Zerk May 15, 1934 2,170,197 Gumprich Aug. 22, 1939 2,172,641 Piron Sept. 12, 1939 2,325,027 Anway July 27, 1943 2,347,780 Hermanns May 2, 1944 

